US4435139A - Screw rotor machine and rotor profile therefor - Google Patents

Screw rotor machine and rotor profile therefor Download PDF

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Publication number
US4435139A
US4435139A US06/345,230 US34523082A US4435139A US 4435139 A US4435139 A US 4435139A US 34523082 A US34523082 A US 34523082A US 4435139 A US4435139 A US 4435139A
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Prior art keywords
flank
rotor
pitch
radius
point
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US06/345,230
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Ake Astberg
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SVENSKA ROTOR MASKINER A CORP OF KINGDOM OF SWEDEN AB
Svenska Rotor Maskiner AB
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Svenska Rotor Maskiner AB
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Assigned to SVENSKA ROTOR MASKINER AKTIEBOLAG, A CORP. OF KINGDOM OF SWEDEN reassignment SVENSKA ROTOR MASKINER AKTIEBOLAG, A CORP. OF KINGDOM OF SWEDEN ASSIGNMENT OF ASSIGNORS INTEREST. Assignors: ASTBERG, AKE
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    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01C—ROTARY-PISTON OR OSCILLATING-PISTON MACHINES OR ENGINES
    • F01C1/00—Rotary-piston machines or engines
    • F01C1/08—Rotary-piston machines or engines of intermeshing engagement type, i.e. with engagement of co- operating members similar to that of toothed gearing
    • F01C1/082—Details specially related to intermeshing engagement type machines or engines
    • F01C1/084—Toothed wheels

Definitions

  • the present invention relates to a screw rotor machine for a working fluid and to the profiles of the rotors therefor.
  • the invention is especially related to such a machine for selective compression and expansion of an elastic working fluid.
  • a screw rotor machine of the above type for an elastic working fluid comprises a casing with a working space provided with spaced apart low pressure and high pressure ports for communication with low pressure and high pressure channels, respectively, and generally composed of at least two intersecting bores with parallel axes, and a number of rotors intermeshing in pairs, disposed in said bores, each rotor having helical lands and intervening grooves with a warp angle of less than 360°.
  • a pair of communicating groove portions of intermeshing rotors form a chevron-shaped chamber having its base end disposed in a fixed plane transverse to the rotor axes, and adjacent to the high pressure port, whereas its apex moves axially as the rotors revolve to vary the volume of the chamber.
  • One rotor of each pair is of female rotor type, i.e. a rotor having at least the major portions of its lands and grooves disposed inside the pitch circle of the rotor.
  • the other rotor of the pair is of male rotor type, i.e. a rotor having at least the major portions of its lands and grooves disposed outside the pitch circle of the rotor.
  • each rotor groove is asymmetric about the radial line drawn from the centre of the rotor through the midmost point of the bottom of the groove and provided with a primary and a secondary flank.
  • the primary flank is the trailing flank of the female rotor groove and the leading flank of the male rotor groove, respectively, when the machine acts as a compressor, and the reverse thereto when the machine acts as an expander, which means that the primary flank forms the peripherally outer wall of the leg of the chevron-shaped chamber composed of a female rotor groove and the peripherally inner wall of the leg of the chamber composed of a male rotor groove, respectively, and the secondary flank forms the other wall of the related leg of the chamber.
  • each female rotor groove comprises a substantial concave portion following an epitrochoidal curve generally generated by a point near the radially outer end of the cooperating primary male rotor flank, a minor portion of the substantial portion extending out to the pitch circle and following a straight radial line, and a convex addendum portion following a circular arc having its centre adjacent to the pitch circle.
  • the cooperating primary flank of a male rotor comprises correspondingly a substantial convex portion following an epitrochoidal curve generally generated by the innermost point of the minor portion of the primary flank of the female rotor groove, a minor convex portion extending to the pitch circle and following a curve being the envelope developed by the straight line defining the minor portion of the primary female rotor groove flank, and a concave dedendum portion generally following a circular arc and having its centre adjacent to the pitch circle.
  • the secondary flank of the groove of the female rotor comprises a substantial concave portion out to the pitch circle and following a circular arc having its centre outside the pitch circle and having a tangent in its point of intersection with the pitch circle which tangent follows a radial line passing throught the centre of the rotor, and a convex addendum portion similar to that of the primary flank of the groove.
  • the cooperating secondary flank of the male rotor comprises a convex substantial portion following the envelope developed by the circular arc defining the substantial portion of the secondary female rotor groove flank consequently having a radial tangent on the pitch circle and a concave dedendum portion similar to that of the primary flank of the land.
  • the variation along the flank of the angle between the tangent to the flank and a radius through the point of tangency as a function of the distance from the pitch circle is of generally hyperbolic type which means that it is substantially constant over the main portion of each flank but increases rapidly within the region thereof adjacent to the pitch circle.
  • the milling cutter will get a fast variation of its angle at its outer end, i.e. a short radius of curvature, and consequently the cutting angels in the most important region of the rotor flanks will be unfavourable resulting in the necessity of relatively wide tolerances within this region.
  • the actual shape of the cutter induces a high wear thereof and thus a considerable amount of tool material has to be ground away during each resharpening operation.
  • the cooperating secondary flank of a male rotor is provided with a corresponding section disposed outside and adjacent to the pitch circle of this rotor and following the envelope developed by the straight line flank section of the female rotor.
  • the angle between the two flanks of a male rotor groove within the region adjacent to the pitch circle is increased up to a value allowing hob milling manufacture simultaneously as the radius of curvature of the secondary male land flank in its point of intersection with the pitch circle obtains a certain length which, however, is only about 60% of the product of the pitch radius and the sine function of said 20° angle whereas the radius of curvature on the primary flank side still is zero.
  • the rotor profile shown in British Pat. No. 1,503,488 is further modified in relation to that shown in British Pat. No. 1,197,432 in that the dedendum portion of the primary flank of each male rotor adjacent to the pitch circle is provided with a section following a straight line directed radially towards the centre of the rotor and in that the addendum portion of the primary flank of each female rotor groove is provided with a corresponding section disposed adjacent to the pitch circle of the rotor and following the envelope developed by said flank section of the primary male rotor flank.
  • Those sections of the primary flanks of the male and female rotors, respectively, are intended for an improvement of so called female rotor drive, i.e.
  • the female rotor is connected to a prime mover and the male rotor is driven by direct flank contact between the rotors, which is intended especially for small compressors in order to increase the number or revolutions of the male rotor and thus the tip speed of the rotors without any need of a step-up gear.
  • the location of those flank sections inside the pitch circle of the male rotor and outside the pitch circle of the female rotor, respectively, is intended to provide meshing conditions between those flank sections favourable for achieving a lubricating liquid film therebetween.
  • the section of the primary flank of the female rotor groove will in its point of intersection with the pitch circle have a radial tangent, and a length of its radius of curvature having a zero value, similar to the conditions for the male rotor land flanks discussed above in relation to the unmodified profile. For this reason the section of the primary female rotor groove flank is impaired by drawbacks of about the same type as those discussed above with regard to the male rotor land flanks. Furthermore, the straight radial section of the primary male rotor land flank will further complicate the cutting of the rotor. Owing to those disadvantages a rotor profile as shown in British Pat. No. 1,503,488 is not suitable for practical use.
  • each flank of the female rotor extends between a point disposed slightly outside the base circle of the involute curve to a point slightly outside the pitch circle.
  • the angle between the two flanks of a male rotor groove is increased at the pitch circle simultaneously as the radii of curvature in the points of intersection between the flanks and the pitch circle gets a certain value, being the product of the pitch radius and the sine function of the pressure angle.
  • the angle between the flanks of the male rotor decreases rapidly when moving inwardly from the pitch circle simultaneously as the variation of the angle between the tangent and the radius still is of generally hyperbolic type which means a rapid increase thereof adjacent to the pitch circle and in to the base circle of the involute.
  • the length of the radius of said arc is of the order of 20% to 40% of the centre distance of the rotors and the centre of said arc is disposed outside the pitch circle of the female rotor, which means that the cooperating flank section of the male rotor land in its point of intersection with the pitch circle has a tangent forming an angle of only about 5° with a radial line drawn from the centre of the rotor through said point of intersection, and further that the radius of curvature of the flank section in said point is very small and amounts to only 60% to 70% of the product of the pitch radius and the sine function of said 5° angle.
  • the variation of the angle between the tangent and the radius is also in this modified profile of hyperbolic type and reaches a high value at the pitch circle.
  • a first main object of the present invention is to achieve a screw rotor machine of the type specified which may be manufactured more accurately and at a lower cost, simultaneously as the efficiency of the machine is improved, compared with earlier produced machines.
  • a second object is to achieve a screw rotor machine which may be adopted not only for male rotor drive but also for female rotor drive with at least the same efficiency and mechanical reliability.
  • a third object is to achieve a rotor profile where each female rotor land has such a shape that its peripheral width increases continuously from its radially outermost to its radially innermost end thereby increasing the stiffness thereof with regard to bending forces.
  • a fourth object is to achieve a continuous movement of the sealing point along each rotor flank from one end thereof to the other as the rotors revolve.
  • the main object of the invention is met by modifying the rotor profile shown in British Pat. No. 1,197,432 at least with regard to the portion of the primary flank of each male rotor groove within the region adjacent to the pitch circle.
  • the pitch point angle i.e. the angle between the tangent to the flank in its point of intersection with the pitch circle and the radial line from the centre of the rotor through this point, falls within the range 0.25 rad to 0.75 rad simultaneously as the radius of curvature of the flank in this point has a length exceeding the product of the pitch radius of the rotor and the sine function of the pitch point angle.
  • flank within the region thereof adjacent the pitch circle has such a shape that the ratio between the angular deviation from the pitch point angle of the angle between the tangent to the flank in an arbitrary point thereof and radial line from the centre of the rotor through this point, and the radial distance from the point to the pitch circle is substantially constant and about equal to the average value of such a ratio taken over the major portion of the flank remote from the pitch circle.
  • the second object of the invention is met by providing the primary male rotor flank with a portion extending on both sides of the pitch circle and having a generally constant radius of curvature. In this way an easily manufactured contact surface can be obtained inside the pitch circle having a considerable radius of curvature and a favourable tangent angle of the same type as discussed above with regard to the main object of the invention.
  • the third object of the invention is met by providing also the secondary male rotor flank with a portion with a generally constant radius of curvature, extending outwardly from the pitch circle and having a pitch point tangent forming an angle of at least 20° with a radial line through the pitch point.
  • the secondary female rotor flank generated thereby will then get an S-shaped configuration resulting in continuous increase of the peripheral width of the female rotor land from its radially outermost to its radially innermost end.
  • the fourth object of the invention is met by replacing the sharp corners of the primary rotor flanks of the profile shown in British Pat. No. 1,197,432 by short arc portions.
  • the flank profile will follow a continuous curve which can be manufactured more accurately and with less risk for damages of the completed rotor, simultaneously as the sealing point moves continuously along all flank portions, resulting in a better sealing action and in a considerable reduction of the leakage area owing to a local defect of the sealing arc-shaped portion compared with the leakage area owing to a similar defect of a sharp corner of the earlier rotor profile.
  • FIG. 1 shows a vertical section through a screw compressor taken on line 1--1 in FIG. 2,
  • FIG. 2 shows a transverse section through the compressor of FIG. 1 taken on line 2--2 in FIG. 1,
  • FIG. 3 shows a detail of FIG. 2 on a larger scale
  • FIG. 4 shows another rotor profile according to the invention
  • FIG. 5 shows a portion of the male rotor shown in FIG. 3,
  • FIG. 6 shows in a diagram the shape of the male rotor flanks in relation to the rotor radius
  • FIG. 7 shows the profile of a cutter blade.
  • the screw compressor shown in FIGS. 1 to 3 comprises a casing 10 forming a working space 12 substantially in the form of two intersecting cylindrical bores having parallel axes.
  • the casing 10 is further provided with a low pressure channel 14 and a high pressure channel 16 for the working fluid which channels communicate with the working space 12 through a low pressure port 18 and a high pressure port 20, respectively.
  • the low pressure port 18 is located in its entirety in the low pressure end wall 22 of the working space 12 and extends mainly on one side of the plane containing the axes of the bores.
  • the high pressure port 20 of the compressor shown is located partly in the high pressure end wall 24 of the working space 12 and partly in its barrel wall 26 and it is in its entirety located on the side of the plane through the axes of the bores opposite to the low pressure port 18.
  • a male rotor 28 and a female rotor 30 located with their axes coinciding with the axes of the bores. These rotors are journaled in the casing 10 in cylindrical roller bearings 32 in the low pressure end wall and in pairs of ball bearings 34 with shoulders in the high pressure end wall 24.
  • the female rotor 30 is further provided with a stub shaft 36 projecting outside the casing 10.
  • the male rotor 28 has four helical lands 38 and intervening grooves 40 having a wrap angle of about 300°.
  • the female rotor 30 has six helical lands 42 and intervening grooves 44 having a wrap angle of about 200°.
  • the female rotor lands 42 are provided with addendums 48 located radially outside the pitch circle 46 of the female rotor 30 and the male rotor grooves 40 are provided with corresponding dedendums 52 located radially inside the pitch circle 50 of the male rotor 28.
  • a plurality of oil injection channels 54 opening at the intersection line 56 between the two bores forming the working space 12. These channels 54 form communications between an oil supply chamber 58 and the working space 12. Oil is supplied to this chamber from a pressure oil source not shown through a supply opening 60 under a pressure higher than the pressure prevailing in the working space 12 at the openings of the channels 54.
  • each male rotor groove 40 comprises a primary flank 62, being the leading flank of the groove when disposed in a compressor and the trailing flank thereof when disposed in an expander, and a secondary flank 64, being the trailing flank or the leading one, respectively.
  • Each of said flanks 62, 64 extends from a radially innermost bottom portion 66 of the groove 40 out to the crest portion 68 of the adjacent land 38.
  • the primary flank 62 is composed of three consecutive portions.
  • the first portion 70-72 of the flank 62 follows a circular arc having a radius r 1 and its centre 74 disposed on a distance b 1 from the centre 76 of the rotor 28 and extend from a point 70 inside the pitch circle 50 disposed on a distance from the centre 76 of the rotor of about 95% of the pitch radius r M of the rotor to a point 72 outside the pitch circle 50 disposed on a distance from the rotor centre 76 of about 110% of the pitch radius r M .
  • the portion 70-72 intersects with the pitch circle 50 in a point 78 and has in this point a tangent which forms an angle ⁇ 1 with a radial line 76-78.
  • the angle ⁇ 1 is 20° or about 0.3 rad.
  • the length of the radius r 1 is about 1.6 times the product of the pitch radius r M and sine ⁇ 1 .
  • the distance b.sub. 1 is somewhat larger than the product of the pitch radius r M and cosine ⁇ 1 .
  • the second portion 72-80 of the flank 62 follows a generally epitrochoidal curve, generated by a section 82-84 of the cooperating primary flank 100 of the female rotor groove 44, and extends from the point 72 where it has a tangent common to that of the first flank portion 70-72 to a point 80 dispoed close to the crest portion 68 of the land 38.
  • the flank section 82-84 follows a circular arc having a radius r s and its center 86 disposed on a distance b s from the centre 88 of the female rotor 30.
  • the length of the radius r s is about 5% of the distance between the centres 76, 88 of the rotors.
  • the distance b s is about equal to the product of the pitch radius r F of the female rotor 30 and ⁇ cosine ⁇ 1 .
  • the radius of curvature of the generally epitrochoidal curve defining the second flank portion 72-80 decreases continuously from the outer point 80 to the inner point 72 where it has a functional minimum equal to the radius r 1 .
  • the third portion 80-68 of the flank 62 follows a circular arc having a radius r 3 and its centre 90 disposed on a distance b 3 from the centre 76 of the rotor 28 and extends from the point 80 where it has a tangent common to that of the second flank portion 72-80 to the crest portion 68.
  • the length of the radius r 3 is about 5% of the distance between the centres 76, 88 of the rotors.
  • the distance b 3 is about equal to the difference between the outer radius of the rotor 28 and the radius r 3 .
  • the secondary flank 64 follows a circular arc having a radius r 2 and its centre 92 disposed on a distance b 2 from the centre 76 of the rotor and extends from a point 94 inside the pitch radius 50 disposed on a distance from the centre 76 of the rotor of about 95% of the pitch radius r M of the rotor to the crest portion 68.
  • the secondary flank 64 intersects with the pitch circle 50 in a point 96 and has in this point a tangent which forms an angle ⁇ 2 with a radial line 76-96.
  • the angle ⁇ 2 is 30° or about 0.5 rad.
  • the length of the radius r 2 is about 1.4 times the product of the pitch radius r M and sine ⁇ 2 .
  • the distance b 2 is somewhat larger than the product of the pitch radius r M and cosine ⁇ 2 .
  • the bottom portion 66 is composed of a major, convex section cylindrical around the centre 76 of the rotor and two minor, concave sections for smooth connections with the primary and secondary flanks of the rotor 28 in the points 70 and 94, respectively.
  • the crest portion 68 follows a convex circular arc having its centre 98 on the pitch circle 50 for smooth connections with the primary and secondary flanks of the rotor 28.
  • Each female rotor groove 44 comprises a primary flank 100, being the trailing flank of the groove when disposed in a compressor and the leading flank thereof when disposed in an expander, and a secondary flank 102, being the leading flank or the trailing one respectively.
  • Each of said flanks 100, 102 extends from a radially innermost bottom portion 104 of the groove 44 out to the crest portion 106 of the adjacent land 42.
  • the primary flank 100 is composed of three consecutive portions.
  • the first portion extending from the crest portion 106 to the point 82 follows a curve generated by the first flank portion 70-72 of the cooperating primary flank 62 of the male rotor 28.
  • the second portion is the flank section 82-84 described above in connection with the second portion 72-80 of the primary flank 62 of the male rotor. It has to be noted that this section 82-84 can be decreased down to zero length whereby, however, this section will be replaced by an obtuse corner.
  • the third portion extending from the point 84 to the bottom portion 104 follows a curve generated by the third portion 80-68 of the cooperating primary flask 62 of the male rotor 28.
  • the secondary flank 102 of the female rotor groove 44 follows a convex-concave curve having a point of inflection generated by the cooperating, secondary flank 64 of the male rotor.
  • the crest portion 106 of the female rotor 30 is composed of a major, convex portion cylindrical around the centre 88 of the rotor and two minor, convex sections for smooth connection with the primary and secondary flanks of the rotor.
  • the bottom portion 104 of the female rotor 30 follows a concave, circular arc having its centre 108 on the pitch circle 46 for smooth connection with the primary and secondary flanks of the rotor 30.
  • the crest portion 68 of the male rotor 28 and the bottom portion 104 of the female rotor 30 are also possible to shape the crest portion 68 of the male rotor 28 and the bottom portion 104 of the female rotor 30 as convex portions cylindrical around the related centre 76, 88 of the rotor. It is also possible to replace the minor convex sections of the female rotor crest 106 and the third portion 80-68 of the primary flank 62 of the male rotor 28 by obtuse corners.
  • FIG. 4 shows a rotor profile of the same general type designed for a combination of a male rotor having five lands and grooves and a female rotor having seven lands and grooves.
  • FIG. 5 A tangent to a male rotor flank at an arbitrary point thereof is shown in FIG. 5.
  • the length of a radial line from the centre 76 of the rotor to this arbitrary point is denoted “r,” and is comprised of the pitch radius "r M " and a distance "e” from the pitch circle to said arbitrary point.
  • the angle between this radial line and the tangent is denoted “ ⁇ + ⁇ " when measured correspondingly to the angle " ⁇ " between the radial line and the tangent at the pitch point, i.e., the point where the flank and the pitch circle intersect (FIG. 3).
  • FIG. 6 shows in a diagram the variation of the ratio " ⁇ /e,” specified above in connection with FIG. 5, as a function of the radial distance “r/r M " from the centre 76 of the rotor to the actual point of tangency.
  • the curve “a” relates to the secondary flank 64 in FIG. 3
  • the curve “b” relates to the primary flank 62 in FIG. 3
  • the curve “c” relates to the corresponding primary flank "116" of the rotor profile shown in FIG. 6 of British Pat. No. 1,197,432
  • curve “d” shows as a comparison the function of a flank similar to that related to curve "c" where the flank portion adjacent to the pitch circle has been replaced by a flank portion of involute type having a pressure angle of 20°.
  • the ratio " ⁇ /e" for the type of primary flank used up to now, curve “c,” follows a function of generally hyperbolic type having an asymptote at the pitch circle.
  • the angular deviation of the angle of the tangent varies very quickly from the radial position of the point of tangency within the region adjacent to the pitch circle.
  • a cutter for production of such a profile also will have a shape where the edge thereof gets a fast variation of its direction and of its radius of curvature which in turn results in very high requirements of the exactness of the cutter for production of a rotor having reasonable tolerances.
  • the secondary flank 64 of the profile shown in FIG. 3 results in a similar function for the ratio " ⁇ /e".
  • curve "a" the function follows over the main portion of the flank inside as well as outside of the pitch circle a substantially straight line and has a practically constant value of about 1.1 which also falls within the range of the formula given above.
  • each male rotor groove By shaping the flanks of each male rotor groove according to the invention the angular deviation of the angle of the tangent varies in proportion to the radial position of the point of tangency, especially within the region of the flank adjacent to the pitch circle and disposed on both sides thereof.
  • a cutter for production of such a profile will have a shape where the edge thereof follows a continuous curve without any fast changes of its direction or of its radius of curvature which in turn results in a very close tolerances of a rotor produced thereby compared with a rotor of the old type shown in FIG. 6 of British Pat. No. 1,197,432 with the same tolerances of the cutters.
  • the quality of the rotors and thereby the efficiency of the screw rotor machine in which they are mounted will be considerably increased without any increase of the manufacturing cost in fact this cost may even be decreased as the new cutter profile is easier and thus cheaper to produce.
  • FIG. 7 This fact is further illustrated in FIG. 7 where the profile of a blade for a profile cutter according to the invention is shown by a continuous line together with the corresponding profile for the old profile discussed above shown by a dashed line.
  • the angle between the two flanks of the cutter blade is much larger for the one according to the invention than for the one according to the old rotor profile.
  • This fact is most dominant at the outer end of the blade where the angle between the flanks has its minimum.
  • the minimum angle of the new blade is about 48° which is about four times that of the old blade which is only about 12°.
  • the shape of the blade profile further means more favourable cutting angles and less wear of the tools which means a higher number of rotors produced between the resharpening operations. Furthermore the new profile admits a wider selection of the angles between the cutting tool and the workpiece during the manufacturing operation which in turn means that the cutting angles will be still more favourable so that the wear of the tool is still more reduced simultaneously as it opens up the possibility to increase the cutting speed. In other words the invention opens up the possibility to manufacture a more efficient machine for a considerably lower cost than that for the old less efficient machine.
  • the first male flank portion has such a radius of curvature that the surface stresses of the rotor flanks are minimized which in combination with a decreased relative sliding speed results in less wear of the rotors during operation of the screw rotor machine.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Rotary Pumps (AREA)
  • Applications Or Details Of Rotary Compressors (AREA)
  • Rotary-Type Compressors (AREA)
US06/345,230 1981-02-06 1982-02-03 Screw rotor machine and rotor profile therefor Ceased US4435139A (en)

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GB8103739 1981-02-06
GB8103739 1981-02-06

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US06/834,219 Reissue USRE32568E (en) 1981-02-06 1986-02-25 Screw rotor machine and rotor profile therefor

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US06/834,219 Expired - Lifetime USRE32568E (en) 1981-02-06 1986-02-25 Screw rotor machine and rotor profile therefor

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JP (1) JPS57148001A (de)
AT (1) AT400974B (de)
AU (1) AU545590B2 (de)
BE (1) BE892039A (de)
BR (1) BR8200606A (de)
CA (1) CA1187461A (de)
CH (1) CH657897A5 (de)
CS (1) CS244420B2 (de)
DD (1) DD161222A5 (de)
DE (1) DE3203228A1 (de)
DK (1) DK50682A (de)
ES (1) ES8302187A1 (de)
FI (1) FI70074C (de)
FR (1) FR2499638B1 (de)
IE (1) IE52830B1 (de)
IN (1) IN157732B (de)
IT (1) IT1153426B (de)
MX (1) MX151158A (de)
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US4583927A (en) * 1983-03-16 1986-04-22 Kabushiki Kaisha Kobe Seiko Sho Screw rotor mechanism
US4636156A (en) * 1984-05-29 1987-01-13 Compair Broomwade Limited Screw rotor machines with specific tooth profiles
US4673344A (en) * 1985-12-16 1987-06-16 Ingalls Robert A Screw rotor machine with specific lobe profiles
US4679996A (en) * 1985-06-29 1987-07-14 Hokuetsu Industries Co., Ltd. Rotary machine having screw rotor assembly
US4890991A (en) * 1987-09-01 1990-01-02 Kabushiki Kaisha Kobe Seiko Sho Screw rotor assembly for screw compressor
EP0276252B1 (de) * 1986-07-08 1990-01-03 Svenska Rotor Maskiner Ab Rotierender schraubenverdichter
US4946362A (en) * 1988-04-25 1990-08-07 Svenska Rotor Maskiner Ab Rotary screw compressor with a lift valve mounted in high pressure end wall
US5556271A (en) * 1994-11-23 1996-09-17 Coltec Industries Inc. Valve system for capacity control of a screw compressor and method of manufacturing such valves
US5624250A (en) * 1995-09-20 1997-04-29 Kumwon Co., Ltd. Tooth profile for compressor screw rotors
US5713724A (en) * 1994-11-23 1998-02-03 Coltec Industries Inc. System and methods for controlling rotary screw compressors
US6257855B1 (en) * 1998-11-19 2001-07-10 Hitachi, Ltd. Screw fluid machine
CN1081296C (zh) * 1998-09-23 2002-03-20 复盛股份有限公司 螺旋转子的齿形创生方法
US6422847B1 (en) * 2001-06-07 2002-07-23 Carrier Corporation Screw rotor tip with a reverse curve
US6529590B1 (en) 1994-11-23 2003-03-04 Coltec Industries, Inc. Systems and methods for remotely controlling a machine
US20030223897A1 (en) * 2002-06-03 2003-12-04 Jim Ferentinos Two-stage rotary screw fluid compressor
US20120017634A1 (en) * 2010-07-20 2012-01-26 Trane International Inc. Variable Capacity Screw Compressor and Method
CN103291619A (zh) * 2013-07-03 2013-09-11 上海齐耀螺杆机械有限公司 一种喷油的双螺杆压缩机转子型线
US20170227009A1 (en) * 2014-06-26 2017-08-10 Svenska Rotor Maskiner Ab Pair of co-operating screw rotors

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* Cited by examiner, † Cited by third party
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US4412796A (en) * 1981-08-25 1983-11-01 Ingersoll-Rand Company Helical screw rotor profiles
JPS59196988A (ja) * 1983-03-16 1984-11-08 Kobe Steel Ltd スクリユ−圧縮機等のスクリユ−ロ−タ
US4663341A (en) * 1984-02-16 1987-05-05 Rohm And Haas Company Insecticidal n-aryl-3-aryl-4,5-dihydro-1h-pyrazole-1-carboxamides
JPH0799147B2 (ja) * 1988-04-05 1995-10-25 株式会社前川製作所 スラスト相殺型スクリュ−圧縮機
AU2003257923B2 (en) * 1998-05-29 2006-09-14 Carrier Corporation Conjugate screw rotor profile

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US4583927A (en) * 1983-03-16 1986-04-22 Kabushiki Kaisha Kobe Seiko Sho Screw rotor mechanism
US4636156A (en) * 1984-05-29 1987-01-13 Compair Broomwade Limited Screw rotor machines with specific tooth profiles
US4679996A (en) * 1985-06-29 1987-07-14 Hokuetsu Industries Co., Ltd. Rotary machine having screw rotor assembly
US4673344A (en) * 1985-12-16 1987-06-16 Ingalls Robert A Screw rotor machine with specific lobe profiles
EP0276252B1 (de) * 1986-07-08 1990-01-03 Svenska Rotor Maskiner Ab Rotierender schraubenverdichter
US4890991A (en) * 1987-09-01 1990-01-02 Kabushiki Kaisha Kobe Seiko Sho Screw rotor assembly for screw compressor
US4946362A (en) * 1988-04-25 1990-08-07 Svenska Rotor Maskiner Ab Rotary screw compressor with a lift valve mounted in high pressure end wall
USRE36281E (en) * 1994-11-23 1999-08-24 Coltec Industries Inc. Valve system for capacity control of a screw compressor and method of manufacturing such valves
US5694682A (en) * 1994-11-23 1997-12-09 Coltec Industries Inc. Method of manufacturing valve system for capacity control of a screw compressor
US5713724A (en) * 1994-11-23 1998-02-03 Coltec Industries Inc. System and methods for controlling rotary screw compressors
USRE36274E (en) * 1994-11-23 1999-08-24 Coltec Industries Inc Method of manufacturing valve system for capacity control of a screw compressor
US6450771B1 (en) 1994-11-23 2002-09-17 Coltec Industries Inc System and method for controlling rotary screw compressors
US6077051A (en) * 1994-11-23 2000-06-20 Coltec Industries Inc System and methods for controlling rotary screw compressors
US5556271A (en) * 1994-11-23 1996-09-17 Coltec Industries Inc. Valve system for capacity control of a screw compressor and method of manufacturing such valves
US6529590B1 (en) 1994-11-23 2003-03-04 Coltec Industries, Inc. Systems and methods for remotely controlling a machine
US5624250A (en) * 1995-09-20 1997-04-29 Kumwon Co., Ltd. Tooth profile for compressor screw rotors
CN1081296C (zh) * 1998-09-23 2002-03-20 复盛股份有限公司 螺旋转子的齿形创生方法
US6257855B1 (en) * 1998-11-19 2001-07-10 Hitachi, Ltd. Screw fluid machine
BE1014896A5 (fr) * 1998-11-19 2004-06-01 Hitachi Ltd Machine a vis pour fluide.
US6422847B1 (en) * 2001-06-07 2002-07-23 Carrier Corporation Screw rotor tip with a reverse curve
US20030223897A1 (en) * 2002-06-03 2003-12-04 Jim Ferentinos Two-stage rotary screw fluid compressor
US20120017634A1 (en) * 2010-07-20 2012-01-26 Trane International Inc. Variable Capacity Screw Compressor and Method
US10941770B2 (en) * 2010-07-20 2021-03-09 Trane International Inc. Variable capacity screw compressor and method
US11022117B2 (en) 2010-07-20 2021-06-01 Trane International Inc. Variable capacity screw compressor and method
US11486396B2 (en) 2010-07-20 2022-11-01 Trane International Inc. Variable capacity screw compressor and method
US11933301B2 (en) 2010-07-20 2024-03-19 Trane International Inc. Variable capacity screw compressor and method
CN103291619A (zh) * 2013-07-03 2013-09-11 上海齐耀螺杆机械有限公司 一种喷油的双螺杆压缩机转子型线
CN103291619B (zh) * 2013-07-03 2015-06-17 上海齐耀螺杆机械有限公司 一种喷油的双螺杆压缩机转子型线
US20170227009A1 (en) * 2014-06-26 2017-08-10 Svenska Rotor Maskiner Ab Pair of co-operating screw rotors
US10451065B2 (en) * 2014-06-26 2019-10-22 Svenska Rotor Maskiner Ab Pair of co-operating screw rotors

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BE892039A (fr) 1982-05-27
CA1187461A (en) 1985-05-21
IE52830B1 (en) 1988-03-16
DD161222A5 (de) 1985-06-26
CH657897A5 (de) 1986-09-30
JPH0250319B2 (de) 1990-11-01
IN157732B (de) 1986-05-24
FI70074B (fi) 1986-01-31
USRE32568E (en) 1987-12-29
NL8200460A (nl) 1982-09-01
DK50682A (da) 1982-08-07
DE3203228C2 (de) 1990-07-19
AU8023082A (en) 1982-08-12
ATA38082A (de) 1995-09-15
JPS57148001A (en) 1982-09-13
IE820254L (en) 1982-08-06
FR2499638A1 (fr) 1982-08-13
CS244420B2 (en) 1986-07-17
ES509360A0 (es) 1982-12-16
BR8200606A (pt) 1982-12-14
FI820378L (fi) 1982-08-07
ES8302187A1 (es) 1982-12-16
DE3203228A1 (de) 1983-01-20
IT8219494A0 (it) 1982-02-05
FR2499638B1 (fr) 1985-07-26
ZA82529B (en) 1983-03-30
AT400974B (de) 1996-05-28
AU545590B2 (en) 1985-07-18
NL191951C (nl) 1996-11-04
NL191951B (nl) 1996-07-01
MX151158A (es) 1984-10-04
FI70074C (fi) 1986-09-12
IT1153426B (it) 1987-01-14

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